CN112041594A - Multi-gear planetary gear for a vehicle having at least one electric machine - Google Patents

Multi-gear planetary gear for a vehicle having at least one electric machine Download PDF

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Publication number
CN112041594A
CN112041594A CN201980030879.5A CN201980030879A CN112041594A CN 112041594 A CN112041594 A CN 112041594A CN 201980030879 A CN201980030879 A CN 201980030879A CN 112041594 A CN112041594 A CN 112041594A
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China
Prior art keywords
gear
clutch
planetary
freewheel
transmission
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Granted
Application number
CN201980030879.5A
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Chinese (zh)
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CN112041594B (en
Inventor
I·克拉斯特耶夫
W·穆罕默德
T·施利滕鲍尔
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Robert Bosch GmbH
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Robert Bosch GmbH
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H37/00—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00
    • F16H37/02—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings
    • F16H37/04—Combinations of toothed gearings only
    • F16H37/042—Combinations of toothed gearings only change gear transmissions in group arrangement
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • B60K1/00—Arrangement or mounting of electrical propulsion units
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • B60K17/00—Arrangement or mounting of transmissions in vehicles
    • B60K17/04—Arrangement or mounting of transmissions in vehicles characterised by arrangement, location, or kind of gearing
    • B60K17/06—Arrangement or mounting of transmissions in vehicles characterised by arrangement, location, or kind of gearing of change-speed gearing
    • B60K17/08—Arrangement or mounting of transmissions in vehicles characterised by arrangement, location, or kind of gearing of change-speed gearing of mechanical type
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60T—VEHICLE BRAKE CONTROL SYSTEMS OR PARTS THEREOF; BRAKE CONTROL SYSTEMS OR PARTS THEREOF, IN GENERAL; ARRANGEMENT OF BRAKING ELEMENTS ON VEHICLES IN GENERAL; PORTABLE DEVICES FOR PREVENTING UNWANTED MOVEMENT OF VEHICLES; VEHICLE MODIFICATIONS TO FACILITATE COOLING OF BRAKES
    • B60T1/00—Arrangements of braking elements, i.e. of those parts where braking effect occurs specially for vehicles
    • B60T1/005—Arrangements of braking elements, i.e. of those parts where braking effect occurs specially for vehicles by locking of wheel or transmission rotation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
    • F16H3/46—Gearings having only two central gears, connected by orbital gears
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
    • F16H3/46—Gearings having only two central gears, connected by orbital gears
    • F16H3/48—Gearings having only two central gears, connected by orbital gears with single orbital gears or pairs of rigidly-connected orbital gears
    • F16H3/52—Gearings having only two central gears, connected by orbital gears with single orbital gears or pairs of rigidly-connected orbital gears comprising orbital spur gears
    • F16H3/54—Gearings having only two central gears, connected by orbital gears with single orbital gears or pairs of rigidly-connected orbital gears comprising orbital spur gears one of the central gears being internally toothed and the other externally toothed
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
    • F16H61/0059—Braking of gear output shaft using simultaneous engagement of friction devices applied for different gear ratios
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • B60K1/00—Arrangement or mounting of electrical propulsion units
    • B60K2001/001—Arrangement or mounting of electrical propulsion units one motor mounted on a propulsion axle for rotating right and left wheels of this axle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/0021—Transmissions for multiple ratios specially adapted for electric vehicles
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
    • F16H2200/0034—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising two forward speeds
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/20—Transmissions using gears with orbital motion
    • F16H2200/2002—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears
    • F16H2200/2005—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears with one sets of orbital gears
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/20—Transmissions using gears with orbital motion
    • F16H2200/203—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes
    • F16H2200/2035—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes with two engaging means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/20—Transmissions using gears with orbital motion
    • F16H2200/203—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes
    • F16H2200/2064—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes using at least one positive clutch, e.g. dog clutch
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/20—Transmissions using gears with orbital motion
    • F16H2200/203—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes
    • F16H2200/2066—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes using one freewheel mechanism
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/20—Transmissions using gears with orbital motion
    • F16H2200/2079—Transmissions using gears with orbital motion using freewheel type mechanisms, e.g. freewheel clutches
    • F16H2200/2082—Transmissions using gears with orbital motion using freewheel type mechanisms, e.g. freewheel clutches one freewheel mechanisms
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/20—Transmissions using gears with orbital motion
    • F16H2200/2094—Transmissions using gears with orbital motion using positive clutches, e.g. dog clutches

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Transportation (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Retarders (AREA)

Abstract

The invention relates to a multi-gear planetary transmission (10). The multi-gear planetary gear (10) comprises a drive shaft (12) having a sun gear (18) and a ring gear (19) and an output shaft (14) having a planet carrier which comprises at least one planet gear (30). The drive shaft (12) and the output shaft (14) can be connected to each other or disconnected from each other by means of a clutch (20). The multi-gear planetary gear (10) has a freewheel (26). By means of this freewheel, the clutch (20) is switched under load between a first transmission ratio i _1 and a second transmission ratio i _ 2.

Description

Multi-gear planetary gear for a vehicle having at least one electric machine
Technical Field
The invention relates to a multi-gear planetary gear for a vehicle having at least one electric machine and a drive shaft with a sun gear and an output shaft with a planetary gear. The invention further relates to the use of the multi-gear planetary transmission integrated into an axle of a vehicle having at least one electric machine.
Background
US 2015/0226297a1 relates to an electric axle on an electric drive of a vehicle. An electric axle for a vehicle driven by electricity is disclosed, the vehicle having an electric machine and two secondary shaft transmissions for driving the wheels of the axle. Downstream of the electric machine, a switchable gear mechanism is arranged, which is embodied as a planetary gear mechanism having a freewheel and a differential. The electric shaft has a shifting mechanism for shifting two gears. In the first gear, the ring gear of the gear mechanism and the clutch body formed on the housing are connected to one another and the clutch between the ring gear and the planet carrier of the gear mechanism is disengaged. In second gear, the ring gear and the clutch body are not connected, and the clutch is closed. The switching according to US 2015/0226297a1 is rather expensive.
Disclosure of Invention
According to the invention, a multi-gear planetary gear set is proposed, wherein the multi-gear planetary gear set has a drive shaft with a sun gear and a ring gear and an output shaft with a planet carrier, which has at least one planet gear. The drive shaft and the output shaft can be connected to each other or disconnected from each other by means of a clutch. The multi-gear planetary gear has a freewheel, by means of which the first gear ratio i _1 and the second gear ratio i _2 are shifted under load by means of a clutch. The multi-gear planetary transmission proposed according to the invention requires only one clutch in order to implement a load changeover between the two gears. In contrast to the solutions according to the prior art, the clutch and the blocking device are not switched for the multi-gear planetary transmission according to the invention, but rather the freewheel is sufficient for the actuation of a single clutch. This reduces the effort for the shift function, which reduces the weight of the proposed multi-gear planetary gear and simplifies the complexity and saves costs by using the freewheel.
In a development of the multi-gear planetary transmission according to the invention, a claw clutch is associated with the freewheel and can lock the freewheel. In particular, when a first gear with a first transmission ratio i _1 is implemented, the freewheel is locked relative to the housing of the multi-gear planetary transmission, wherein the clutch is disengaged. The first transmission ratio i _1 is produced by the relation i _1=1- (z _ H/z _ S), where z _ H denotes the number of teeth of the ring gear and z _ S denotes the number of teeth of the sun gear.
If a second gear ratio i _2 is to be engaged in the second gear of the multi-gear planetary transmission according to the invention, the clutch is closed and the freewheel is released. The second transmission ratio i _2 is produced by i _2=1, which means that all sun gears, i.e. the ring gear, the sun gear and the planet gear carrier rotate equally fast and no rotational speed differences occur.
In addition to the first and second gears, the multi-gear planetary transmission according to the invention can also be shifted into reverse. For this purpose, for example, in the case of a vehicle having an electric motor, the electric motor can be driven in reverse, the clutch being disengaged and the freewheel being locked by a locking device associated therewith.
In addition, the multi-gear planetary transmission according to the invention can also be switched to the parking lock function. For this purpose, the clutch is closed and the freewheel is locked by a locking device.
In a further embodiment of the multi-gear planetary gear according to the invention, the clutch comprises a first clutch element and a second clutch element. In a first embodiment variant, the first clutch element is received on the drive shaft and the second clutch element is received on the planet carrier shaft of the planetary gear. In a second embodiment of the clutch, the first clutch element is likewise received on the drive shaft, while the second clutch element is received on the output shaft.
The multi-gear planetary gear set proposed according to the invention can be arranged in an axially parallel arrangement with respect to the axle. The multi-gear planetary transmission according to the invention can drive a differential transmission via one or more spur gear stages. In a further embodiment, the multi-gear planetary gear set can be integrated into the axle and drive the bevel gears of the directly driven differential gear set.
The invention further relates to the use of the multi-gear planetary transmission on an axle of a vehicle having at least one electric machine.
The multi-gear planetary gear set according to the invention is distinguished by a comparatively simple switchability with which both the first and the second transmission ratio can be realized on the output side. Furthermore, the reverse gear and parking lock function can be achieved by the multi-gear planetary transmission which is proposed according to the invention and can be easily switched under load. The multi-gear planetary gear set proposed according to the invention is also characterized by a reduced weight, and the use of the freewheel greatly simplifies the complexity and makes it possible to achieve cost savings. A locking device is associated with the freewheel, so that it can be locked relative to the housing, which allows reversing by means of a counter-rotation of the at least one electric machine. Allowing the at least one motor to rotate in both directions also represents a small expense.
In its design as a planetary gear, the multi-gear planetary gear according to the invention has the highest power density of all gears, can be switched under load without tension interruption and thus advantageously makes it possible to use a freewheel and a non-positive disk clutch. In particular, it is emphasized that the freewheel can be adjusted very easily.
Drawings
The invention is described in detail below with the aid of the figures.
Wherein:
fig. 1 shows a schematic representation of a multi-gear planetary transmission received between a drive shaft and an output shaft;
FIGS. 2.1 and 2.2 show possible designs of the clutch;
fig. 3 shows a spur gear stage assigned to the multi-gear planetary transmission proposed according to the invention for driving a differential transmission; and is
Fig. 4 shows an integrated arrangement of the multi-gear planetary gear in the axle.
Detailed Description
The illustration according to fig. 1 shows a multi-gear planetary gear set 10, which is received between a drive shaft 12 and an output shaft 14.
The multi-gear planetary gear set 10 is received in a housing 16. On the drive shaft 12 there is a sun gear 18 and a first clutch element 22 of a clutch 20. The sun gear 38 meshes with at least one planet gear 30 which comprises the planet carrier shaft 32 and which surrounds in the ring gear 19. The planet carrier shaft 32 is connected on the one hand to the output shaft 14 and on the other hand has the second clutch element 24 of the clutch 20. The at least one planetary gear 30 meshes with the freewheel 26, to which a locking device 28, which is provided, for example, as a claw clutch, is assigned. The at least one planetary gear 30 can be embodied as a single, double or stepped planetary gear.
Fig. 2.1 and 2.2 show an embodiment variant of the multi-gear planetary transmission 10 according to the invention.
As can be seen from the illustration according to fig. 2.1, the clutch 20 comprises a first clutch part 22, which is received on the drive shaft 12. The first clutch part 22 of the clutch 20 interacts with a second clutch part 24, which in the embodiment variant according to fig. 2.1, like the illustration in fig. 1, is located on a planet carrier shaft 32 of at least one planet wheel 30. The sun gear 18 received on the drive shaft 12 meshes with at least one planet gear 30, to which the freewheel 26 is assigned, which can be locked with a locking device 28 relative to the housing 16.
In the embodiment variant of the multi-gear planetary transmission 10 proposed according to the invention, which is shown in fig. 2.2, a shaft-side clutch 34 is formed. In the embodiment variant shown in fig. 2.2, the first clutch element 22 is located on the shaft end of the drive shaft 12. And the second clutch member 24 is received on the shaft end of the output shaft 14. In the embodiment of the multi-gear planetary transmission 10 according to fig. 2.2, in which the sun gear 18 received on the drive shaft 12 is in mesh with at least one planet gear 30, the planet gear is assigned the freewheel 26, which can be locked with respect to the housing 16 by means of the locking device 28, in a similar manner to the previous embodiment. The carrier shaft 32 received on the at least one planet gear 20 is connected with the output shaft 14. The operating principle of the multi-gear planetary transmission according to the invention shown in fig. 1, 2.1 and 2.2 is described below:
the first gear in the transmission ratio i _1=1- (z _ H/z _ S) can be realized by: the clutch 20 is disengaged and the freewheel 26 is locked with respect to the housing 16 of the multi-gear planetary gear 10 by means of a locking device 28. z _ H denotes the number of teeth of the ring gear 19, and z _ S denotes the number of teeth of the sun gear 18 of the multi-speed planetary transmission.
The second gear with the transmission ratio i _2=1 is implemented by: the clutch 20 is closed and the freewheel 26 is released. In this case, all sun gears of the multi-stage planetary gear 10 rotate equally fast without a difference in rotational speed.
In addition, the multi-gear planetary transmission 10 proposed according to the invention, which can be shifted under load, can also be operated in reverse gear. For this purpose, for example, for a vehicle having at least one electric motor 40, which rotates in the reverse direction, the clutch 20 is in the disengaged state and the freewheel 26 is locked relative to the housing 16 by activation of the locking device 28. Due to the at least one electric machine 40 rotating in the opposite direction, in this shift position of the assembly a reverse gear can be achieved, wherein similarly to the first gear in the forward direction a transmission ratio i _ R =1- (z _ H/z _ S) is achieved.
However, this corresponds to the transmission ratio i _1 in the first gear, which is the reverse gear due to the at least one oppositely rotating electric machine 40.
In addition, with the multi-gear planetary transmission 10 according to the invention, the parking lock function can be implemented by: the clutch 20 is in the closed state and the freewheel 26 is locked by means of a catch 28. In this case, the transmission is blocked and the drive shaft 12 and the output shaft 14 cannot rotate because they are braked.
As can be seen from the illustration according to fig. 3, the multi-stage planetary gear 10 is arranged in an axially parallel arrangement 46 with respect to the axle 58. The at least one electric motor 40 drives a first spur gear stage 42, which in turn drives the drive shaft 12 of the multi-gear planetary transmission 10. On which the first clutch element 22 and the sun gear 18 are arranged. The sun gear 18 meshes with at least one planet gear 30, to which the freewheel 26 is assigned, which can be locked relative to the housing 16 of the multi-gear planetary gear 10 by means of a locking device 28. The at least one planetary gear 30 has a planet carrier shaft 32 which is connected on the one hand to the output shaft 14 of the multi-gear planetary gear 10 and on the other hand receives the second clutch element 24 of the clutch 20. The output shaft 14 is connected to a differential gear mechanism 48 via a further second spur gear stage 44. The differential drive has a first bevel gear 50, a second bevel gear 52, a third bevel gear 54 and a fourth bevel gear 56. The differential gear 48 in turn drives the first and second shaft elements 60, 62 of the axle 58 on which the first wheel 64 or the second wheel 66 is located.
Fig. 4 shows the integration of the proposed load-shiftable multi-gear planetary transmission 10 into the axle 58. As can be gathered from fig. 4, the electric motor 40 is coaxial with the axle 58. The motor 40 includes a stator 70 and a rotor 68. The rotor 68 is connected to the drive shaft 12 of the multi-gear planetary gear set 10. The multi-speed planetary gear set is in a coaxial arrangement 74 with the first and second shaft elements 60 and 62 of the axle 58. The multi-gear planetary gear set 10 depicted in fig. 4 with dashed lines is constructed analogously to the multi-gear planetary gear set 10 shown in fig. 1, 2.1 and 2.2. As can be seen from the illustration according to fig. 4, the multi-stage planetary gear 10 comprises two planetary gears 30 which mesh with the sun gear 18 received on the drive shaft 12. A free-wheel mechanism 26 is assigned to each of the planetary gears 30 of the multi-stage planetary gear 10, which are shown in fig. 4, and can be locked with respect to the housing 16 of the multi-stage planetary gear 10 by means of a separate locking device 28. In the representation of the multi-gear planetary gear set 10 according to fig. 4, the clutch 20 is designed such that the first clutch element 22 is located on the circumference of the drive shaft 12, see also the representation of the multi-gear planetary gear set according to fig. 2.1.
Fig. 4 shows that in this embodiment variant the planet carrier shafts 32 of the planet wheels 30 function as a direct drive for the directly driven differential gear 72. In the embodiment variant shown in fig. 4, the carrier shaft 32 and the output shaft 14, as shown in fig. 1, 2.1 and 2.2 on the multi-stage planetary gear 10, coincide as one component. Via a directly driven differential gear 72, as shown in fig. 4, the first axle element 60 and thus the first wheel 64 and the second wheel 66 are each driven via the second axle element 62. This results from the arrangement shown in fig. 4, namely: the electric motor 40, the multi-gear planetary gear set 10 and the directly driven differential gear set 72 represent a modular unit, a so-called electric axle.
For the sake of completeness, it is mentioned that the directly driven differential gear 72, like the differential gear shown in fig. 3 which is driven by the spur gear stages 42, 44, comprises a first bevel gear 50, a second bevel gear 52 and a third bevel gear 54 and a fourth bevel gear 56. On the output side, the first shaft element 60 is driven by the directly driven differential gear 72 via the second bevel gear 52 and the second shaft element 62 is driven via the fourth bevel gear 56.
The multi-gear planetary gear set 10 described above, although shown as a reduction gear, can include all forms of a single planetary gear set according to VDI 21572012-10, i.e. for example an accelerator, a reduction gear or a reduction gear with multi-stage planetary gears.
The present invention is not limited to the embodiments described herein and the aspects emphasized therein. Rather, a number of modifications are possible within the scope of the claims and within the reach of the person skilled in the art.

Claims (13)

1. Multi-gear planetary gear (10) having a drive shaft (12) with a sun gear (18) and a ring gear (19) and having an output shaft (14) with a planet carrier, which comprises at least one planet gear (30), wherein the drive shaft (12) and the output shaft (14) can be connected to and disconnected from each other by means of a clutch (20), characterized in that the multi-gear planetary gear (10) has a freewheel (26) by means of which a changeover takes place under load between a first transmission ratio i _1 and a second transmission ratio i _2 by means of the clutch (20).
2. The multi-gear planetary gear (10) according to claim 1, characterized in that a locking device (28) is associated with the freewheel (26), which locks the freewheel (26).
3. The multi-gear planetary gear set (10) according to claim 1, characterized in that the clutch (20) is disengaged and the freewheel (26) is locked relative to the housing (16) of the multi-gear planetary gear set (10) for the first transmission ratio i _ 1.
4. The multi-speed planetary transmission (10) according to claim 1, characterized in that the clutch (20) is closed and the freewheel (26) is released for the second transmission ratio i _ 2.
5. The multi-gear planetary transmission (10) according to claims 1 and 2, characterized in that the reverse gear is produced by an electric motor (40) of the vehicle driven in the reverse direction, the clutch (20) being in the disengaged state and the freewheel (26) being locked by a locking device (28).
6. The multi-gear planetary transmission (10) according to claim 1, characterized in that the parking lock function is realized by a closed clutch (20) and a freewheel (26) locked by a locking device (28).
7. The multi-speed planetary transmission (10) according to claim 1, characterized in that the clutch (20) has a first clutch means (22) and a second clutch means (24).
8. The multi-speed planetary transmission (10) according to claim 7, characterized in that the first clutch means (22) is received on the drive shaft (12) and the second clutch means (24) is received on a planet carrier shaft (32) of the planetary gear (30).
9. The multi-speed planetary transmission (10) according to claim 7, characterized in that the first clutch means (22) is received on the drive shaft (12) and the second clutch means (24) is received on the output shaft (14).
10. The multi-gear planetary transmission (10) according to claim 1, characterized in that it is arranged in an axis-parallel arrangement (46) with respect to the axle (58).
11. The multi-speed planetary transmission (10) according to claim 10, characterized in that it drives a differential transmission (48) via one or more spur gear stages (42, 44).
12. The multi-gear planetary gear (10) according to claim 1, characterized in that it is integrated into an axle (58) and drives the bevel gears (50, 54) of a directly driven differential gear (72).
13. Use of a multi-speed planetary transmission (10) according to any of claims 1 to 12 on an axle (58) of a vehicle having at least one electric machine (40).
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PCT/EP2019/061036 WO2019214995A1 (en) 2018-05-08 2019-04-30 Multi-speed planetary transmission for a vehicle with at least one electric machine

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Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102021202258A1 (en) * 2021-03-09 2022-09-15 Zf Friedrichshafen Ag electric drive
DE102021203417A1 (en) * 2021-04-07 2022-04-07 Zf Friedrichshafen Ag Transmission for a vehicle
DE102021203416A1 (en) * 2021-04-07 2022-10-13 Zf Friedrichshafen Ag Transmission for a vehicle
US11364797B1 (en) * 2021-06-09 2022-06-21 Arvinmeritor Technology, Llc Multi-speed axle assembly having a one-way freewheel clutch
DE102022202378A1 (en) * 2022-03-10 2023-09-14 Zf Friedrichshafen Ag Transmission for a vehicle and drive train with such a transmission
US11712955B1 (en) * 2022-08-18 2023-08-01 Dana Belgium N.V. Multi-speed electric axle and electric axle shifting strategy

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102010001259A1 (en) * 2009-07-30 2011-02-10 Zf Friedrichshafen Ag Transmission oil pump for an automatic transmission and method for operating the transmission oil pump
CN102562972A (en) * 2010-10-26 2012-07-11 通用汽车环球科技运作有限责任公司 Multi-speed transmission module
DE102012216132A1 (en) * 2012-09-12 2014-03-13 Schaeffler Technologies AG & Co. KG Wheel hub drive and wheel with wheel hub drive
CN105209283A (en) * 2013-03-13 2015-12-30 美国轮轴制造公司 Two-speed drive module
CN106471281A (en) * 2014-07-04 2017-03-01 Zf腓德烈斯哈芬股份公司 Many gears actuating device for rail vehicle
CN107599823A (en) * 2017-10-19 2018-01-19 吉林大学 Differential multimodal fusion power car drive system

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102007007037A1 (en) * 2007-02-08 2008-08-14 Iav Gmbh Ingenieurgesellschaft Auto Und Verkehr planetary gear
DE102014101713A1 (en) 2014-02-12 2015-08-13 Dr. Ing. H.C. F. Porsche Aktiengesellschaft Electric portal axle for the electric drive of a motor vehicle

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102010001259A1 (en) * 2009-07-30 2011-02-10 Zf Friedrichshafen Ag Transmission oil pump for an automatic transmission and method for operating the transmission oil pump
CN102562972A (en) * 2010-10-26 2012-07-11 通用汽车环球科技运作有限责任公司 Multi-speed transmission module
DE102012216132A1 (en) * 2012-09-12 2014-03-13 Schaeffler Technologies AG & Co. KG Wheel hub drive and wheel with wheel hub drive
CN105209283A (en) * 2013-03-13 2015-12-30 美国轮轴制造公司 Two-speed drive module
CN106471281A (en) * 2014-07-04 2017-03-01 Zf腓德烈斯哈芬股份公司 Many gears actuating device for rail vehicle
CN107599823A (en) * 2017-10-19 2018-01-19 吉林大学 Differential multimodal fusion power car drive system

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
曾显恒: "《汽车电器系统故障检测与修复》", 30 October 2015 *

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DE102018207110A1 (en) 2019-11-14
EP3791093A1 (en) 2021-03-17

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